EP0232677B1 - Brûleur, notamment brûleur pour la combustion de combustibles liquides en état gazeux - Google Patents

Brûleur, notamment brûleur pour la combustion de combustibles liquides en état gazeux Download PDF

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Publication number
EP0232677B1
EP0232677B1 EP86810577A EP86810577A EP0232677B1 EP 0232677 B1 EP0232677 B1 EP 0232677B1 EP 86810577 A EP86810577 A EP 86810577A EP 86810577 A EP86810577 A EP 86810577A EP 0232677 B1 EP0232677 B1 EP 0232677B1
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EP
European Patent Office
Prior art keywords
burner according
fuel
burner
gasification chamber
drive shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP86810577A
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German (de)
English (en)
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EP0232677A1 (fr
Inventor
Jörg Füllemann
Heinrich Boner
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VTH AG Verfahrenstechnik fur Heizung
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VTH AG Verfahrenstechnik fur Heizung
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Priority to AT86810577T priority Critical patent/ATE45417T1/de
Publication of EP0232677A1 publication Critical patent/EP0232677A1/fr
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Publication of EP0232677B1 publication Critical patent/EP0232677B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
    • F23D11/04—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying action being obtained by centrifugal action
    • F23D11/06—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying action being obtained by centrifugal action using a horizontal shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
    • F23D11/005—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space with combinations of different spraying or vaporising means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
    • F23D11/24—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space by pressurisation of the fuel before a nozzle through which it is sprayed by a substantial pressure reduction into a space
    • F23D11/26—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space by pressurisation of the fuel before a nozzle through which it is sprayed by a substantial pressure reduction into a space with provision for varying the rate at which the fuel is sprayed

Definitions

  • the invention relates to a burner, in particular a burner for burning liquid fuels in the gaseous state, with a motor for driving a fan and / or a fuel pump, with a carburetor chamber formed by a housing and having at least one heatable wall, with one in the carburetor chamber arranged rotatable device, the drive shaft is coupled to the motor, and with a jacket surrounding the drive shaft, which serves as a fuel supply member in the carburetor chamber.
  • a burner is described in EP-A-O 136 522.
  • atomizer burners are sprayed with a nozzle and burned in a combustion chamber with the supply of air. Since the atomizing performance of the nozzle can only be varied within narrow limits, atomizing burners have the disadvantage that their performance cannot be regulated continuously. Nor can they be built for very low power. The smallest nozzles are designed for an oil consumption of around 1.4 kg per hour. Since the output of the atomizer burner cannot be regulated continuously, atomizer burners are operated intermittently with low heat requirements. Since the operating intervals cannot be chosen as short as required, relatively large boilers are required as energy stores.
  • the intermittent operation has the disadvantage that the repeated starting and switching off of the burner brings heavy temperature changes to the materials as well as a high soot and pollutant load for the boiler, chimney and environment. Incomplete combustion and soot formation, which occur particularly during the start-up phase, have a significant impact on the overall efficiency of a heating system. Furthermore, the radiation losses from the large boilers further reduce the overall efficiency.
  • gasification burners In contrast to the atomizer burners described, gasification burners generally have the advantage that they can be regulated continuously down to very low outputs in accordance with the heating requirement. Furthermore, a significant reduction in the emission of pollutants, for example unburned hydrocarbons and soot, is achieved in the combustion of gasified fuel.
  • gasification burners Despite the many advantages that gasification burners have, they are only used to a small extent. A major reason for this is that most gasification burners need a lot of maintenance. Gasification burners usually tend to form undesirable deposits in the gasification chamber, which will soon significantly affect the effectiveness of the gasification and thus the operation of the burner.
  • EP-A-0 036 128 describes a gasification burner with an electrically heatable gasification chamber.
  • the temperature of this gasification chamber is measured by a temperature sensor and kept at an optimal value by means of a control device in order to avoid coking of fuel.
  • Another measure to avoid coking is that the gasification chamber has no air inlet openings.
  • a rotatable device in the form of a wiper is accommodated in the gasification chamber. This wiper is used to finely distribute the fuel on the heated carburetor walls and to prevent the formation of deposits, so that there is no harmful influence of deposits on the evaporation of the fuel.
  • the gas formed in the gasification chamber leaves the chamber through a nozzle at a relatively high speed.
  • the combustion air is conveyed by a fan.
  • a modified form of this gasification burner is described in the aforementioned EP-A-O 136 522.
  • the burners described in these documents have the disadvantage that they require a relatively large amount of electrical energy to evaporate the fuel. Burners of this type are also relatively expensive because they require a temperature sensor and a temperature controller.
  • the combustion of the gas emerging from a nozzle at a relatively high speed has the disadvantage that it causes relatively high noise.
  • cold start problems can arise because the air is not heated or is only slightly heated before combustion.
  • after-burning of gasified fuel with a sooting flame can take place, unless particularly expensive measures are taken to prevent the further escape of gasified fuel from the pressurized gasification chamber.
  • EP-AO 067 271 shows a continuously adjustable oil burner with an electrically heated evaporation device which has air inlet openings and which is monitored by a thermostat.
  • This evaporation device is cup-shaped, air inlet openings being provided on the bottom of the cup.
  • This cup there is a rotating cylinder for oil distribution.
  • This cylinder fills the evaporator space in the cup to a small gap.
  • oil is fed to the rotating cylinder via a hollow drive shaft, which is then thrown by centrifugal force from the radial bores in the rotating cylinder onto the inner walls of the evaporator chamber.
  • oil burners of this type have not found commercial use.
  • the gasification chamber tends to become contaminated, whereby the air inlet or the air / gas mixture outlet is disturbed. Since the pressure difference between the air inlet and the air / gas mixture outlet is very small, even slight contamination leads to a sooty flame.
  • Another disadvantage is that the rotating cylinder absorbs a great deal of heat via the cylinder jacket surface and via the drive shaft leads to the drive motor, which can be damaged if costly devices are not taken to protect it.
  • the need for thermostat monitoring of the carburetor also contributes to increasing the purchase costs for the burner.
  • US Pat. No. 3,640,673 describes a burner for a petroleum oven in which a fan is arranged in the gasification chamber which can be heated electrically and by the flame of the burner. There is a relatively large space between the periphery of the fan and the heated wall surface of the gasification chamber. There is a spray disc for the fuel on the drive shaft for the fan. When fuel is sprayed onto the spray disc during operation, it distributes the fuel into fine droplets that are thrown outwards by centrifugal force. They are mixed by the fan with the preheated air flowing into the gasifier chamber. Since the distance between the periphery of the fan and the heated wall surface of the gasification chamber is relatively large, most fuel droplets evaporate without ever coming into contact with a wall surface.
  • a gasification burner in which a rotor provided with blades, the blades of which extend into the vicinity of the heatable wall of the gasification chamber, is arranged.
  • the carburetor chamber has an air inlet.
  • the fuel supplied via the rotor shaft is finely distributed by the rotor and mixed with compressed air, whereby it evaporates in the hot gasification chamber.
  • the mixture can then escape through openings in a burner plate at relatively high pressure and burn with a low-noise blue flame.
  • a mixing tube and a flame tube are provided coaxially with the nozzle.
  • the oil is injected through the nozzle into the mixing tube, into which the air necessary for combustion is also blown.
  • a flame then forms at the end of the mixing tube.
  • Part of the hot combustion gases is then recirculated to the beginning of the mixing tube and mixed there with the oil mist / air mixture for the purpose of heat exchange. Thanks to the recirculation of some of the combustion gases, this burner enables the oil droplets in the mixing tube to be largely gasified and thus better combustion with less soot formation.
  • it cannot be regulated over a wide performance range and requires a relatively high oil throughput in the lowest performance range.
  • the burner described offers additional problems when starting and stopping. This is all the more serious because the burner has to be operated intermittently.
  • the mixing tube is cold and therefore has no vaporizing effect. The flame is therefore sooty until the mixing tube has reached a high temperature and is able to evaporate the oil that hits it.
  • the oil dripping from the nozzle is re-burned with a strongly sooting flame.
  • the mixing tube near the nozzle is still glowing bright red when it is switched off, it radiates a lot of heat towards the nozzle, which can lead to coking of fuel in the nozzle. This can clog the nozzle, especially if it is a small nozzle.
  • this is achieved in a burner of the type mentioned at the outset in that the carburetor-side end of the casing has a first axial bearing surface, that the rotatable device has a second axial bearing surface, and in that adjusting means are provided in order to move the two axial bearing surfaces apart or towards one another to let fuel into the carburettor chamber or shut off the fuel supply according to the heat demand.
  • the burner therefore does not require a nozzle and avoids the disadvantages associated with it, such as the risk of clogging, lack of controllability, impossibility of operation in a low power range, incomplete combustion and soot formation, etc.
  • the rotating axial bearing surface ensures a good distribution of the fuel in the carburettor chamber, which causes the ensures complete gasification of the fuel.
  • the amount of fuel delivered per unit of time can easily be regulated by the delivery pressure. Since there is a relative movement between the axial bearing surfaces during operation, there is no risk of clogging. After-burning is avoided when the burner is switched off because the thrust bearing surfaces are close together and no longer allow fuel to flow out. An extremely simple construction is possible, which does not require high-precision parts such as atomizer nozzles. Since the axial bearing surfaces at Ab rub against each other, self-cleaning takes place.
  • the adjusting means are expediently formed by a hydraulic device and a spring.
  • the hydraulic device advantageously consists of a recess in an axial bearing surface. Fuel can thus flow into this recess during operation and generate a pressure which drives the two axial bearing surfaces apart and enables the fuel to exit. This construction is extremely simple and cheap.
  • the spring is advantageously a helical spring arranged in a space between the drive shaft and the casing, one end of which rests on a flange or adjusting ring of the drive shaft and the other end on a slide ring, which in turn rests on a shoulder of the casing.
  • the carburetor end of the jacket is advantageously formed by a ceramic tube.
  • This can also be designed as a bearing for the drive shaft of the rotatable device.
  • Such training proves to be expedient because relatively high temperatures occur in this area.
  • a spray edge is advantageously formed on the periphery of the second axial bearing surface. This allows the oil droplets to be torn off easily during rotation and thus promotes a fine distribution of the fuel.
  • the carburetor chamber is provided with an air inlet in the region of the jacket surrounding the drive shaft.
  • the mixing of fuel and air before combustion enables the burner to operate quietly.
  • the air supply in the vicinity of the drive shaft cools it and thus protects the bearings and the motor.
  • a recirculation inlet is expediently additionally arranged at the air inlet, a coaxial arrangement being particularly simple and expedient.
  • This enables recirculation of hot exhaust gases, which heats up the carburettor housing and the carburetor chamber.
  • This has the advantage that no electrical heating is necessary after the start-up phase.
  • the heat of vaporization is therefore supplied by the flame.
  • the build-up of deposits is prevented by strongly heating the carburetor housing.
  • the suffering frost effect prevents the microscopic oil droplets from touching the hot wall. Instead, the oil droplets dance on a kind of air cushion until they have completely evaporated.
  • the desired strong heating of the carburetor chamber wall can be achieved in particular by arranging the recirculation inlet on the periphery of the air inlet.
  • An electrical heater for the starting phase is expediently arranged on the wall of the carburetor housing at the recirculation inlet. Since hot gases recirculate immediately after the flame has formed, the electrical heating
  • the carburetor housing is advantageously formed by a cylindrical or conical tube. This results in a particularly simple and cheap construction of the carburetor housing.
  • the inside of the tube is advantageous with a larger surface insert, e.g. a metal mesh. This facilitates the evaporation of the fuel.
  • the rotatable device in the evaporator chamber it proves to be advantageous to further design the rotatable device as a rotor provided with blades, the blades of which extend up to the proximity of the inner wall of the tube is sufficient. An even better distribution of the fuel is then achieved by means of this rotor.
  • a device that can be controlled by a heating controller, e.g. a pressure reducing valve provided to regulate the pressure in the fuel supply line.
  • the pressure can be regulated between approximately 0.5 and 5 bar, which corresponds to regulating the output in a ratio of 1 to 10. This regulation can thus be carried out in a simple and reliable manner using very simple means. Since operation with a throughput of approximately 0.1 kg of fuel per hour is also possible, the burner can also be used where so-called cup burners were previously used. Cup burners burn with a strongly sooting flame, produce exhaust gases that are heavily contaminated, are not very reliable and require a lot of maintenance work. Replacing cup burners with environmentally friendly and reliable burners is therefore an old but not yet achieved goal.
  • a particularly simple embodiment of the invention is characterized in that the casing has two bearings arranged at a distance from one another for mounting the drive shaft, between which a space is arranged, that a connection for the pressure side of the fuel pump is provided between the bearings and that a passage from the space mentioned is arranged to the recess in the axial bearing surface.
  • This simple construction is particularly suitable in the event that work is carried out with low pressures. At low pressures, there are hardly any sealing problems, so that a construction in which a connection is provided for the suction side of the fuel pump can be dispensed with.
  • the device that can be controlled by the heating control is a so-called Volustat with particular advantage.
  • This is understood to mean a device which, according to an input signal, delivers a corresponding delivery volume which is practically not influenced by resistances in the delivery line.
  • the delivery volume is hardly influenced by the viscosity of the fuel.
  • a Volustat it is possible to keep the force required to move the two axial bearing surfaces apart or towards one another to a minimum. In other words, this means that a relatively soft spring with a flat spring characteristic can be used.
  • pressures of about 0.3 to 0.8 bar are generated with a fuel throughput of 0.4 to 2.5 kg per hour.
  • the burner shown in the drawing has a motor II which serves to drive the fuel pump 13, the fan 15 and the rotatable device 17.
  • the rotating device 17 is part of an easily replaceable unit 12.
  • the rotating device 17 is connected via the drive shaft 19 and the coupling 21 to the motor shaft, which is not visible in the drawing.
  • a jacket 23 enclosing the drive shaft 19 serves as a fuel supply element in a carburetor chamber 25.
  • the jacket 23 is formed by the adapter sleeve 27 and a ceramic tube 29 inserted at the end of the adapter tube on the carburetor side.
  • the ceramic tube is firmly connected to the adapter sleeve by the screw 31 and also serves as a bearing for the drive shaft 19.
  • the jacket 23 could also consist of a piece of metal.
  • a ceramic bearing 29 has the advantage that it is very heat-resistant and can therefore withstand the high temperatures in the carburetor chamber 25.
  • Another bearing 33 for the drive shaft 19 is arranged in the vicinity of the motor-side end of the adapter sleeve 27.
  • a mechanical seal 35 is located in front of this bearing.
  • a lip seal 37 is arranged at a distance behind the bearing 33.
  • connection 41 leads to the space 43 between the two bearings 29 and 33.
  • Another connection 45 is used to extract any leakage oil from the space 47 between the bearing 33 and the seal 37.
  • the line 49 leads from the connection 45 to the suction side of the fuel pump 13.
  • axial bearing surfaces 51 and 53 are provided both on the ceramic tube 29 and on the rotatable device 17, and that adjusting means are provided in order to move these axial bearing surfaces 51, 53 apart or towards one another in order to produce fuel in accordance with the heat requirement let the jacket 23 in the carburetor chamber 25.
  • a recess 55 on an axial bearing surface 53 and a helical spring 57 in the space 43 between the drive shaft 19 and the adapter sleeve 27 serve as adjusting means.
  • One end of the helical spring 57 rests on the adjusting ring 59, which is fastened to the drive shaft 19 with a screw 61.
  • the other end of the coil spring 57 bears against a slide ring 63 which bears against an end face of the bearing 29.
  • the coil spring 65 serves to press the mechanical seal 35 against the bearing 33.
  • the coil spring 57 acts on the adjusting ring 59 and is therefore endeavored to press the axial bearing surface 53 against the axial bearing surface 51. As long as this pressure is high enough, no fuel can flow into the carburetor chamber 25. However, if the oil pressure in the chamber formed by the recess 55 is large enough, it moves the device 17 against the force of the spring 57 in the axial direction to the right, so that the two axial bearing surfaces 51 and 53 move apart and release a gap through the fuel can flow into the carburetor chamber 25. The higher the pressure in the line 39, the more the gap opens and the more fuel flows into the carburetor chamber 25. To enable this flow, a groove 67 extends in the axial direction from the chamber 43 to the recess 55 in the device 17.
  • the fuel droplets are thrown in the radial direction in the gasifier chamber 25 at high speed by the centrifugal force.
  • the spraying of the fuel is further facilitated by the fact that a spraying edge 69 is provided on the periphery of the axial bearing surface 51.
  • the carburetor chamber 25 has an annular air inlet 71 in the area of the bearing 29. Coaxial with this air inlet 71 is an annular recirculation inlet 73 through which hot fuel gases came into the gasifier from the flame can flow back. At the recirculation inlet 73, an electrical heater 77 is arranged on the wall of the carburetor housing 75.
  • the carburetor housing 75 is formed by an approximately cylindrical or conical tube. The inside of this tube 75 is provided with a surface-increasing insert 79, for example a metal mesh. This facilitates the evaporation of the fuel.
  • a flame tube 81 is provided coaxially and at a distance from the carburetor chamber. The flame tube 81 is divided by a ring 83 into a front part 85 and a rear part 87. In the front part 85, which forms the actual flame tube, there is a tubular insert 89 made of heat-insulating ceramic fibers.
  • a support 93 is fastened on the adapter sleeve 27 with the screws 91 and carries the ignition electrode 95 and the air screen 96.
  • the air inlet 71 is located in the air panel 96.
  • the rotatable device 17 is designed as a rotor provided with blades 98.
  • the blades 98 extend into the vicinity of the inner wall of the carburetor housing 75. They bring about a good mixing of fuel, air and recirculated gas, the mixture compressed by the blades 98 being able to flow out through an annular opening 99 between the carburetor housing 75 and the rotor 17.
  • the rotor 17 is fastened with a screw 18 at the end of the drive shaft 19.
  • the end of the rotor 17 is covered by a plate 20.
  • the flame tube 81 can be easily removed from the fan housing 14 by loosening screws 16.
  • the unit 12 can also be removed after loosening the fuel line connections 41, 45 and the screw 24.
  • This unit 12 essentially comprises the casing 23 with all the mechanics, the carburetor 25 and the ignition electrode 95.
  • a device 22 that can be controlled by the heating controller 26 is provided in order to regulate the fuel supply.
  • the commercially available fuel pumps usually have means, e.g. a pressure reducing valve, with which the desired pump pressure can be set manually.
  • an actuator is provided in the burner according to the present exemplary embodiment.
  • the controllable device 22 consists of an actuator and the means mentioned for setting the pump pressure.
  • the device 22 can be actuated by the heating control 26.
  • the actuator is a solenoid, with which the pump pressure is changed, for example, from 2 bar to 4 bar according to the heat requirement.
  • the burner then works as a two-stage burner. When using two solenoids, four different levels are also possible. However, if a servomotor is used, it is possible to continuously regulate the pump pressure from, for example, 0.5 to 5 bar.
  • the heater control 26 first turns on the electric heater 77 for about two minutes. During this time, the heater 77 and the adjacent insert 79 are heated to approximately 550 ° . After this preheating time has elapsed, the actual starting phase takes place in the usual way as with an atomizer burner.
  • the pressure of the fuel in the recess 55 causes a force which tends to move the rotor 17 to the right in the axial direction against the force of the coil spring 57, so that a gap is opened between the axial bearing surfaces 51 and 53 by the fuel in the carburetor chamber 25 is thrown.
  • the oil droplets strike the hot surface of the insert 79, an oil vapor is formed which is mixed with the combustion air by the rotor 17.
  • the oil throughput can be changed in individual stages or continuously depending on the heating requirement.
  • the helical spring 57 causes the rotor 17 to move axially to the left, so that the axial bearing surface 51 rests on the axial bearing surface 53 and no more fuel can escape. This reliably prevents afterburning.
  • FIG. 2 It has already been mentioned in the description of FIG. 2 that the flame tube 81 can be easily removed from the fan housing 14 by loosening screws 16.
  • the unit 12 can also be easily removed.
  • Figure 3 now shows a preferred embodiment of the unit 12. It is structurally much simpler than the unit 12 shown in Figure 2 and therefore also significantly cheaper to manufacture.
  • the rotatable device 17 is in turn driven by the motor II (FIG. I) of the burner via the drive shaft 19 and the clutch 21.
  • a the drive shaft 19th enclosing jacket 23 serves as a fuel supply member in the carburetor chamber 25.
  • the jacket 23 is formed by the adapter sleeve 27 and the bearings 29 and 33.
  • the bearings 29 and 33 advantageously consist of a suitable bearing material, for example a sintered material. It would also be possible to form the jacket 23 from a single piece of metal.
  • a lip seal 37 is fastened by means of a spring ring 36.
  • connection 41 is provided, to which the line 39 can be connected, which is used to supply fuel.
  • axial bearing surfaces 51 and 53 are provided, and that adjusting means are provided in order to move these axial bearing surfaces 51, 53 apart or towards one another in order to admit fuel from the jacket 23 into the carburetor chamber 25.
  • a recess 55 in an axial bearing surface 51 and, on the other hand, a helical spring 57 serve as adjusting means.
  • One end of the helical spring 57 rests on the adjusting ring 59, which is fastened with a screw 61 on the drive shaft 19.
  • the other end of the coil spring 57 bears against a slide ring 63 which bears against an end face of the bearing 33.
  • the helical spring 57 acts on the adjusting ring 59 connected to the drive shaft 19 and therefore endeavors to press the axial bearing surface 51 against the axial bearing surface 53. As long as this pressure is high enough, no fuel can flow into the carburetor chamber 25. However, if the oil pressure in the chamber formed by the recess 55 is large enough, it moves the device 17 against the force of the spring 57 in the axial direction to the right, so that the two axial bearing surfaces 51 and 53 move apart and release a gap through the fuel can flow into the carburetor chamber 25. The higher the pressure of the line 39, the more the gap opens and the more fuel flows into the carburetor chamber 25.
  • a groove 67 extends in the axial direction from the chamber 43 to the recess 55. Since the device 17 rotates during operation, the fuel droplets are thrown at high speed in the radial direction into the carburetor chamber 25 by the centrifugal force. The spraying of the fuel is further facilitated in that a spraying edge 69 is provided on the rotating part 70.
  • the rotating part 70 is firmly connected to the drive shaft 19 with the screw 18 together with the device 17.
  • the carburetor chamber 25 has an annular air inlet 71 in the area of the bearing 29. This air inlet is formed by the conical part 72 of the air screen 96.
  • This conical configuration results in an advantageous air flow into the gasification chamber, which favors the recirculation of the hot fuel gases.
  • Coaxial with the air inlet 71 is namely an annular recirculation inlet 73 through which the hot fuel gases can flow back into the gasification chamber 25 from the flame.
  • an electrical heater 77 is arranged on the wall of the carburetor housing 75.
  • the carburetor housing 75 is formed by an approximately cylindrical tube.
  • the inside of this tube 75 is provided with a surface-increasing insert 79, e.g. a metal mesh.
  • the flame tube 81 surrounding the unit 12 is indicated by dash-dotted lines in FIG. With regard to the flame tube 81, reference is made to the description of FIG. 2.
  • a support 93 is fastened with screws 91, which supports the ignition electrode 95 (FIG. 2) (not shown in FIG. 3) and the air panel 96.
  • the rotatable device 17 is also designed as a rotor provided with blades 98.
  • a Volustat is advantageously used as the controllable device 22. It is a device that delivers a delivery volume corresponding to an applied control signal.
  • the spring 57 When using a Volustat, the spring 57 only has to perform a closing function when the burner is switched off. The spring 57 can thus have a flat spring characteristic and be relatively soft. As a result, there are only slight pressures in the jacket 23. With a small burner, they range from about 0.2 to about 0.6 bar, corresponding to a fuel throughput of 0.4 to 2.5 kg per hour. At these pressures, the seal 37 is generally sufficient, so that further sealing measures, such as are provided in the exemplary embodiment in FIG. 2, can generally be dispensed with.
  • a Volustat 22 could also be used in combination with a unit 12 according to FIG. 2.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Spray-Type Burners (AREA)
  • Pre-Mixing And Non-Premixing Gas Burner (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Combustion Of Fluid Fuel (AREA)
  • Evaporation-Type Combustion Burners (AREA)
  • Pressure-Spray And Ultrasonic-Wave- Spray Burners (AREA)

Claims (22)

1. Brûleur, comportant un moteur (11) pour l'entrai- nement d'un ventilateur (15) et/ou d'une pompe à combustible (13), une chambre de gazéification (25) qui est formée par un carter (75) et qui présente au moins une paroi chauffable, un dispositif rotatif (17) qui est disposé dans la chambre de gazéification (35) et dont l'arbre d'entraînement (19) est accouplé au moteur (11), et une enveloppe (23) qui entoure l'arbre d'entraînement (19) et qui sert d'organe d'amenée de combustible dans la chambre de gazéification (25), caractérisé en ce que l'extrémité de l'enveloppe (23) du côté gazéification présente une première surface de palier axial (51), en ce que le dispositif rotatif (17) présente une seconde surface de palier axial (53), et en ce qu'il est prévu des moyens de réglage (55, 57) pour déplacer les deux surfaces de palier axial (55, 57) dans le sens de leur écartement et de leur rapprochement, afin d'injecter du combustible dans la chambre de gazéification (25) en fonction des besoins en chaleur ou de couper l'alimentation en combustible.
2. Brûleur selon la revendication 1, caractérisé en ce que les moyens de réglage comprennent un dispositif hydraulique (55) et un ressort (57).
3. Brûleur selon la revendication 2, caractérisé en ce que le dispositif hydraulique est constitué par un évidement (55) dans l'une des surfaces de palier axial (53).
4. Brûleur selon la revendication 2 ou 3, caractérisé en ce que le ressort (57) est un ressort hélicoïdal disposé dans un espace (43) entre l'arbre d'entraînement (19) et l'enveloppe (23), ressort qui s'applique, par l'une de ses extrémités, sur un collet ou bague de butée (59) de l'arbre d'entraînement (19) et, par son autre extrémité, sur un anneau de glissement (63) qui s'applique à son tour sur un gradin de l'enveloppe (23).
5. Brûleur selon l'une quelconque des revendications 1 à 4, caractérisé en ce qu'une arête de pulvérisation (69) est formée à la périphérie de l'une des surfaces de palier axial (51, 53).
6. Brûleur selon l'une quelconque des revendications 1 à 5, caractérisé en ce que l'extrémité de l'enveloppe (23) du côté gazéificateur est constituée par un tube en céramique (39).
7. Brûleur selon la revendication 6, caractérisé en ce que le tube en céramique (39) est réalisé en même temps sous forme de palier pour l'arbre d'entraînement (19) du dispositif rotatif (17).
8. Brûleur selon l'une quelconque des revendications 1 à 7, caractérisé en ce que la chambre de gazéification (25) présente une admission d'air (71) dans la région de l'enveloppe (23) qui entoure l'arbre d'entraînement (19).
9. Brûleur selon la revendication 8, caractérisé en ce que la chambre de gazéification (35) présente une admission de gaz de recirculation (73).
10. Brûleur selon la revendication 9, caractérisé en ce que l'admission d'air (71) et l'admission de gaz de recirculation (73) sont disposées coaxialement l'une par rapport à l'autre.
11. Brûleur selon la revendication 10, caractérisé en ce que l'admission de gaz de recirculation (73) est disposée à la périphérie de l'admission d'air (71).
12. Brûleur selon l'une quelconque des revendications 9 à 11, caractérisé en ce qu'un dispositif de chauffage électrique (77) est disposé près de l'admission de gaz de recirculation (73) sur la paroi du carter du gazéificateur (75).
13. Brûleur selon l'une quelconque des revendications 1 à 12, caractérisé en ce que le carter du gazéificateur (75) est constitué par un tube approximativement cylindrique ou conique.
14. Brûleur selon la revendication 13, caractérisé en ce que le côté intérieur du tube (75) est muni d'une garniture qui en augmente la surface, par exemple d'un tissu métallique (79).
15. Brûleur selon l'une quelconque des revendications 1 à 14, caractérisé en ce que le dispositif rotatif (17) est un rotor muni d'ailettes (98), dont les ailettes (98) s'étendent jusqu'à proximité de la paroi intérieure du tube (75).
16. Brûleur selon la revendication 15, caractérisé en ce qu'une fente (99) pour l'échappement du mélange gaz/air est ménagée entre l'extrémité du rotor et le carter du gazéificateur (75).
17. Brûleur selon l'une quelconque des revendications 1 à 16, caractérisé en ce qu'un tube de flammes (81) est disposé coaxialement et à distance de la chambre de gazéification (25).
18. Brûleur selon l'une quelconque des revendications 1 à 17, caractérisé en ce qu'un dispositif (22) commandable par une commande automatique de chauffage (26) est prévu pour la commande de l'alimentation en combustible.
19. Brûleur selon l'une quelconque des revendications 7 à 18, caractérisé en ce qu'un autre palier (33) est disposé à proximité de l'extrémité de l'enveloppe (23) du côté moteur, et en ce qu'il est prévu sur l'enveloppe (23), du côté de l'autre palier (33) éloigné du moteur, un raccord (41) pour le côté refoulement de la pompe de combustible (13) et, de l'autre côté de l'autre palier (33), un raccord (45) pour le côté aspiration de la pompe de combustible (13).
20. Brûleur selon l'une quelconque des revendications 1 à 5, caractérisé en ce que l'enveloppe (23) présente deux paliers (29, 33) disposés à distance l'un de l'autre pour le montage de l'arbre d'entraînement (19), paliers (29, 33) entre lesquels est formé un espace (43') qui sert de conduit de combustible, en ce qu'un raccord (41) pour l'arrivée de combustible est prévu entre les paliers (29, 33), et en ce qu'un passage (67) est formé entre ledit espace (43') et l'évidement (55) dans la surface de palier axial (53).
21. Brûleur selon l'une quelconque des revendications 8 à 20, caractérisé en ce que l'admission d'air (71) présente une partie conique (72).
22. Brûleur selon l'une quelconque des revendications 18 à 21, caractérisé en ce que le dispositif commandable par une commande automatique de chauffage est un volustat.
EP86810577A 1985-12-30 1986-12-10 Brûleur, notamment brûleur pour la combustion de combustibles liquides en état gazeux Expired EP0232677B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86810577T ATE45417T1 (de) 1985-12-30 1986-12-10 Brenner, insbesondere brenner zur verbrennung von fluessigen brennstoffen in gasfoermigem zustand.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH556885 1985-12-30
CH5568/85 1985-12-30

Publications (2)

Publication Number Publication Date
EP0232677A1 EP0232677A1 (fr) 1987-08-19
EP0232677B1 true EP0232677B1 (fr) 1989-08-09

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EP86810577A Expired EP0232677B1 (fr) 1985-12-30 1986-12-10 Brûleur, notamment brûleur pour la combustion de combustibles liquides en état gazeux

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US (1) US4712997A (fr)
EP (1) EP0232677B1 (fr)
AT (1) ATE45417T1 (fr)
DE (1) DE3664956D1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0283435B1 (fr) * 1987-03-13 1991-01-23 Füllemann Patent Ag Brûleur
US5154597A (en) * 1987-03-13 1992-10-13 Vth Ag Verfahrenstechnik Fur Heizung Burner for combustion of gasified liquid fuels
US5015173A (en) * 1988-06-09 1991-05-14 Vth Ag Verfahrenstechnik Fur Heizung Burner for the combustion of liquids in the gaseous state
EP0595419B1 (fr) * 1992-10-30 1999-05-26 Shell Internationale Researchmaatschappij B.V. Brûleur à combustible liquide
US5834869A (en) * 1997-06-02 1998-11-10 Emerson Electric Co. Blower motor housing
ATE260442T1 (de) * 1998-09-01 2004-03-15 Toby Ag Brenner für flüssige brennstoffe
US8070480B2 (en) * 2003-11-21 2011-12-06 Associated Physics Of America, Llc Method and device for combusting liquid fuels using hydrogen
ES1135492Y (es) * 2014-12-11 2015-04-13 Eika S Coop Foco radiante adaptado a una encimera de cocción

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1648923A (en) * 1924-10-06 1927-11-15 Penberthy Injector Co Oil burner
US3021892A (en) * 1959-01-07 1962-02-20 Gen Thermique Procedes Brola S Burner apparatus
US3640673A (en) * 1969-07-22 1972-02-08 Matsushita Electric Ind Co Ltd Liquid fuel burner
DE2700671C2 (de) * 1977-01-08 1988-07-28 Deutsche Forschungs- und Versuchsanstalt für Luft- und Raumfahrt e.V., 5000 Köln Blaubrennender Ölbrenner
DE3164957D1 (en) * 1980-03-14 1984-08-30 Stoechio Matic Ag Burner for the combustion of liquid fuels in the gaseous state
DE3123078A1 (de) * 1981-06-11 1982-12-30 Buderus Ag, 6330 Wetzlar Stufenlos regelbarer oelgeblaesebrenner
US4509914A (en) * 1981-12-14 1985-04-09 Stoechio-Matic Ag Apparatus for the combustion of liquid fuels in the gaseous state
DE3565002D1 (en) * 1984-06-25 1988-10-20 Vth Ag Burner, especially a burner for burning liquid fuel in the gaseous state

Also Published As

Publication number Publication date
DE3664956D1 (en) 1989-09-14
EP0232677A1 (fr) 1987-08-19
ATE45417T1 (de) 1989-08-15
US4712997A (en) 1987-12-15

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